WO2019155805A1 - Cycle de réfrigération à éjecteur et soupape de réglage de débit - Google Patents

Cycle de réfrigération à éjecteur et soupape de réglage de débit Download PDF

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Publication number
WO2019155805A1
WO2019155805A1 PCT/JP2019/000270 JP2019000270W WO2019155805A1 WO 2019155805 A1 WO2019155805 A1 WO 2019155805A1 JP 2019000270 W JP2019000270 W JP 2019000270W WO 2019155805 A1 WO2019155805 A1 WO 2019155805A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
suction
pressure
flow rate
evaporator
Prior art date
Application number
PCT/JP2019/000270
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English (en)
Japanese (ja)
Inventor
照之 堀田
陽一郎 河本
大介 櫻井
陽平 長野
航 袁
Original Assignee
株式会社デンソー
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Priority claimed from JP2018091449A external-priority patent/JP7031482B2/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2019155805A1 publication Critical patent/WO2019155805A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series

Definitions

  • the present disclosure relates to an ejector refrigeration cycle including an ejector, and a flow rate adjusting valve applied to the ejector refrigeration cycle.
  • an ejector refrigeration cycle which is a vapor compression refrigeration cycle equipped with an ejector
  • the pressure of the refrigerant sucked into the compressor can be increased by the pressure increasing action of the diffuser portion of the ejector.
  • the power consumption of the compressor can be reduced and the coefficient of performance (COP) of the cycle can be improved.
  • Patent Document 1 discloses an ejector-type refrigeration cycle that is applied to an air conditioner and cools blown air that is blown into an air-conditioning target space.
  • the ejector refrigeration cycle of Patent Document 1 includes a branching portion that branches the flow of the high-pressure refrigerant that has flowed out of the radiator, and a suction-side evaporator that evaporates the low-pressure refrigerant and cools the blown air. Yes. Then, one refrigerant branched at the branching portion flows into the nozzle portion of the ejector, and the other refrigerant branched at the branching portion is depressurized by the suction side decompression portion and flows into the suction side evaporator. Further, the refrigerant has a cycle configuration in which the refrigerant flowing out from the suction side evaporator is sucked from the refrigerant suction port of the ejector.
  • Patent Document 1 employs a temperature expansion valve that adjusts the throttle opening degree so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator approaches a predetermined reference superheat degree as the suction side pressure reducing unit. Examples are also disclosed.
  • the refrigerant sucked from the refrigerant suction port of the ejector can be reliably made into a gas phase refrigerant having a superheat degree. According to this, it can suppress that the flow volume (mass flow rate) of the refrigerant
  • the flow rate of the refrigerant flowing into the suction-side evaporator may decrease, so that the temperature distribution of the blown air cooled by the suction-side evaporator may increase. That is, even if the throttle opening degree of the suction side pressure reducing unit is adjusted so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator approaches a predetermined reference superheat degree as in Patent Document 1, cycle load fluctuation Accordingly, there is a possibility that the flow rate of the refrigerant flowing into the suction side evaporator cannot be adjusted appropriately.
  • an object of the present disclosure is to provide an ejector refrigeration cycle in which the flow rate of the refrigerant flowing into the suction side evaporator can be appropriately adjusted.
  • Another object of the present disclosure is to provide a flow rate adjusting valve capable of appropriately adjusting the flow rate of the refrigerant flowing into the suction side evaporator when applied to an ejector refrigeration cycle.
  • the ejector refrigeration cycle includes a compressor, a radiator, an ejector, a suction-side decompression unit, a suction-side evaporator, a bypass path that leads, and a variable throttle mechanism.
  • the compressor compresses and discharges the refrigerant.
  • the radiator dissipates heat from the refrigerant discharged from the compressor.
  • the ejector sucks the refrigerant from the refrigerant suction port by the suction action of the jet refrigerant jetted from the nozzle part that decompresses the refrigerant that has flowed out of the radiator, and the mixed refrigerant of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port. Increase the pressure.
  • the suction side decompression unit decompresses the refrigerant.
  • the suction side evaporator evaporates the refrigerant decompressed by the suction side decompression unit and causes the refrigerant to flow out to the refrigerant suction port side.
  • the bypass passage guides the refrigerant on the inlet side of the suction side decompression unit to the inlet side of the suction side evaporator, bypassing the suction side decompression unit.
  • the variable throttle mechanism adjusts the flow rate of the refrigerant flowing through the bypass passage.
  • the suction-side decompression unit changes the throttle opening so that the superheat degree of the refrigerant on the outlet side of the suction-side evaporator approaches a predetermined reference superheat degree.
  • the variable throttle mechanism has a function of opening and closing the bypass passage, and opens the bypass passage when the flow rate of the refrigerant flowing out from the suction-side decompression portion is equal to or lower than a predetermined reference flow rate.
  • variable throttle mechanism closes the bypass passage under the operating condition in which the flow rate of the refrigerant flowing out from the suction-side decompression unit is larger than the reference flow rate as in normal operation. Thereby, the refrigerant decompressed by the suction side decompression unit can flow into the suction side evaporator.
  • the suction side decompression unit changes the throttle opening, so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator becomes the reference superheat.
  • the flow rate of the refrigerant flowing into the suction side evaporator can be appropriately adjusted so as to approach the degree.
  • variable throttle mechanism opens the bypass passage when the operating condition is such that the flow rate of the refrigerant flowing out from the suction-side decompression unit is below the reference flow rate, such as during low-load operation.
  • entrance of a suction side pressure reduction part can be flowed into a suction side evaporator via a bypass channel.
  • the ejector refrigeration cycle includes a compressor, a radiator, an ejector, a suction-side decompression unit, a suction-side evaporator, and a bypass passage.
  • the compressor compresses and discharges the refrigerant.
  • the radiator dissipates heat from the refrigerant discharged from the compressor.
  • the ejector sucks the refrigerant from the refrigerant suction port by the suction action of the jet refrigerant jetted from the nozzle part that decompresses the refrigerant that has flowed out of the radiator, and the mixed refrigerant of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port.
  • the suction side decompression unit decompresses the refrigerant.
  • the suction side evaporator evaporates the refrigerant decompressed by the suction side decompression unit and causes the refrigerant to flow out to the refrigerant suction port side.
  • the bypass passage guides the refrigerant on the inlet side of the suction side decompression unit to the inlet side of the suction side evaporator, bypassing the suction side decompression unit.
  • the suction-side decompression unit has a sealed space in which a temperature-sensitive medium whose pressure changes with a change in temperature of the refrigerant on the outlet side of the suction-side evaporator is enclosed, and a throttle valve that is displaced according to the pressure of the temperature-sensitive medium.
  • the throttle opening is changed so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator approaches a predetermined reference superheat degree.
  • the value obtained by subtracting the saturation pressure of the temperature-sensitive medium at a predetermined reference medium temperature from the outlet-side pressure, which is the pressure of the refrigerant flowing out of the suction-side evaporator, is defined as the valve opening set pressure, and the maximum passage cut-off of the suction-side decompression unit
  • the ratio of the minimum passage cross-sectional area of the bypass passage to the area is defined as an area ratio X, ⁇ 170X + 3 ⁇ Y and Y ⁇ ⁇ 350X-9.
  • both the refrigerant decompressed by the suction side decompression unit and the refrigerant that has passed through the bypass passage can be caused to flow into the suction side evaporator.
  • the suction side pressure reducing unit increases the throttle opening. For this reason, the ratio of the flow volume of the refrigerant
  • the suction side decompression unit changes the throttle opening, so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator becomes the reference superheat.
  • the flow rate of the refrigerant flowing into the suction side evaporator can be appropriately adjusted so as to approach the degree.
  • the suction-side decompression unit decreases the throttle opening when the operating condition is such that the flow rate of the refrigerant flowing into the suction-side evaporator is relatively low, such as during low-load operation. For this reason, the ratio of the flow rate of the refrigerant
  • the flow rate adjustment valve is configured to suck the refrigerant from the refrigerant suction port by the suction action of the jet refrigerant injected from the nozzle portion that depressurizes the refrigerant, and the suction refrigerant sucked from the jet refrigerant and the refrigerant suction port This is applied to an ejector-type refrigeration cycle having an ejector for increasing the pressure of the mixed refrigerant and a suction side evaporator for evaporating the refrigerant to flow out to the refrigerant suction port side.
  • the flow rate adjusting valve includes a suction side pressure reducing unit, a bypass passage, and a variable throttle mechanism.
  • the suction-side decompression unit changes the throttle opening so that the superheat degree of the refrigerant on the outlet side of the suction-side evaporator approaches a predetermined reference superheat degree.
  • the bypass passage guides the refrigerant on the inlet side of the suction side decompression unit to the outlet side of the suction side decompression unit by bypassing the suction side decompression unit.
  • the variable throttle mechanism adjusts the flow rate of the refrigerant flowing through the bypass passage.
  • the refrigerant inlet side of the suction side evaporator is connected to the evaporator side outlet from which the refrigerant decompressed by the suction side decompression unit flows out.
  • variable throttle mechanism has a function of opening and closing the bypass passage, and bypasses when the flow rate of the refrigerant flowing from the suction-side decompression unit to the refrigerant inlet side of the suction-side evaporator is equal to or lower than a predetermined reference flow rate. Open the passage.
  • variable throttle mechanism unit is Close the bypass passage. Thereby, the refrigerant decompressed by the suction side decompression unit can flow out to the suction side evaporator side.
  • the suction-side decompression unit changes the throttle opening, It is possible to appropriately adjust the flow rate of the refrigerant flowing into the suction side evaporator so that the superheat degree of the refrigerant on the outlet side of the side evaporator approaches the reference superheat degree.
  • variable throttle mechanism unit when the applied ejector-type refrigeration cycle has an operating condition in which the flow rate of the refrigerant flowing out from the suction-side decompression unit is equal to or lower than the reference flow rate as in low load operation, the variable throttle mechanism unit is open. Thereby, the refrigerant
  • the applied ejector-type refrigeration cycle has an operating condition in which a relatively small amount of refrigerant flows into the suction-side evaporator, even if the suction-side decompression unit reduces the throttle opening,
  • the refrigerant that has passed through the passage can surely flow into the suction-side evaporator. Thereby, it can suppress that the flow volume of the refrigerant
  • a flow rate adjustment valve capable of appropriately adjusting the flow rate of the refrigerant flowing into the suction-side evaporator when applied to the ejector-type refrigeration cycle in accordance with the load fluctuation of the cycle. be able to.
  • the flow rate adjusting valve is configured to suck the refrigerant from the refrigerant suction port by the suction action of the jet refrigerant injected from the nozzle portion that depressurizes the refrigerant, and to suck the refrigerant that is sucked from the jet refrigerant and the refrigerant suction port.
  • This is applied to an ejector-type refrigeration cycle having an ejector for increasing the pressure of the mixed refrigerant and a suction side evaporator for evaporating the refrigerant to flow out to the refrigerant suction port side.
  • the flow rate adjusting valve includes a suction side pressure reducing unit and a bypass passage.
  • the suction-side decompression unit includes a sealed space in which a temperature-sensitive medium whose pressure changes with a change in temperature of the refrigerant on the outlet side of the suction-side evaporator is enclosed, and a throttle valve that is displaced according to the pressure of the temperature-sensitive medium.
  • the refrigerant inlet side of the suction side evaporator is connected to the evaporator side outlet through which the refrigerant decompressed by the suction side decompression unit flows out.
  • the value obtained by subtracting the saturation pressure of the temperature-sensitive medium at a predetermined reference medium temperature from the outlet-side pressure, which is the pressure of the refrigerant flowing out of the suction-side evaporator, is defined as the valve opening set pressure, and the maximum passage cut-off of the suction-side decompression unit
  • the ratio of the minimum passage cross-sectional area of the bypass passage to the area is defined as an area ratio X, ⁇ 170X + 3 ⁇ Y and Y ⁇ ⁇ 350X-9.
  • both the refrigerant decompressed by the suction side decompression unit and the refrigerant that has passed through the bypass passage can flow out to the refrigerant inlet side of the suction side evaporator.
  • the suction-side decompression unit reduces the throttle opening. increase. For this reason, the ratio of the flow rate of the refrigerant
  • the suction side decompression unit changes the throttle opening, It is possible to appropriately adjust the flow rate of the refrigerant flowing into the suction side evaporator so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator approaches the reference superheat degree.
  • the suction-side decompression unit when the applied ejector-type refrigeration cycle has an operating condition in which a relatively small amount of refrigerant flows from the suction-side decompression unit to the suction-side evaporator as in low-load operation, the suction-side decompression The part reduces the throttle opening. For this reason, the ratio of the flow volume of the refrigerant
  • the applied ejector-type refrigeration cycle has an operating condition in which a relatively small flow rate of refrigerant flows into the suction-side evaporator, even if the suction-side decompression unit reduces the throttle opening,
  • the refrigerant that has passed through the bypass passage can surely flow into the suction side evaporator. Thereby, it can suppress that the flow volume of the refrigerant
  • a flow rate adjusting valve capable of appropriately adjusting the flow rate of the refrigerant flowing into the suction side evaporator according to the load fluctuation of the cycle when applied to the ejector refrigeration cycle. be able to.
  • FIG. 1 It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is typical sectional drawing at the time of the flow regulating valve of a 1st embodiment making a bypass passage fully closed. It is a typical sectional view at the time of the flow regulating valve of a 1st embodiment making a bypass passage the throttling state. It is typical sectional drawing when the flow regulating valve of a 1st embodiment has made a bypass passage into a full open state. It is a typical sectional view at the time of the flow regulating valve of a 2nd embodiment making a bypass passage fully open. It is typical sectional drawing at the time of the flow regulating valve of a 3rd embodiment making a bypass passage fully open.
  • FIGS. 1-4 1st Embodiment of this indication is described using FIGS. 1-4.
  • the ejector-type refrigeration cycle 10 of this embodiment is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior that is a space to be air-conditioned. Therefore, the fluid to be cooled in the ejector refrigeration cycle 10 is blown air.
  • the ejector refrigeration cycle 10 employs an HFO refrigerant (specifically, R1234yf) as a refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure of the cycle does not exceed the critical pressure of the refrigerant. Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant. A part of the refrigeration oil circulates in the cycle together with the refrigerant.
  • HFO refrigerant specifically, R1234yf
  • the compressor 11 sucks in refrigerant, compresses it, and discharges it. More specifically, the compressor 11 of the present embodiment is an electric compressor that is configured by housing a fixed capacity type compression mechanism and an electric motor that drives the compression mechanism in one housing.
  • the electric motor is a motor whose rotation speed (that is, refrigerant discharge capacity) is controlled by a control signal output from the air conditioning control device 40, and any type of an AC motor or a DC motor can be adopted. Good.
  • the refrigerant inlet side of the radiator 12 is connected to the discharge port of the compressor 11.
  • the radiator 12 is a heat exchanger for condensing by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (outside air) blown by the cooling fan 12a to dissipate the high-pressure refrigerant and condense it.
  • the cooling fan 12 a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device 40.
  • the inlet side of the branch portion 13 is connected to the refrigerant outlet of the radiator 12.
  • the branch part 13 branches the flow of the refrigerant that has flowed out of the radiator 12.
  • the branch part 13 has a three-way joint structure having three refrigerant inlets and outlets communicating with each other, one of the three refrigerant inlets and outlets being a refrigerant inlet and the other two being refrigerant outlets. .
  • the inlet side of the nozzle part 14 a of the ejector 14 is connected to one refrigerant outlet of the branch part 13.
  • the other refrigerant outlet of the branch part 13 is connected to the refrigerant inlet 21 a side formed in the body part 21 of the flow rate adjusting valve 20.
  • the ejector 14 has a nozzle portion 14a for depressurizing and injecting the refrigerant flowing out of the radiator 12, and functions as a refrigerant depressurizing portion. Further, the ejector 14 functions as a refrigerant circulation section that sucks and circulates the refrigerant from the outside by the suction action of the refrigerant injected from the refrigerant injection port of the nozzle portion 14a.
  • the ejector 14 converts the kinetic energy of the mixed refrigerant of the refrigerant injected from the nozzle portion 14a and the suction refrigerant sucked from the refrigerant suction port 14c into pressure energy, and increases the pressure of the mixed refrigerant. It fulfills the function as a part.
  • the ejector 14 has a nozzle portion 14a and a body portion 14b.
  • the nozzle portion 14a is formed of a substantially cylindrical metal (stainless alloy in the present embodiment) that gradually tapers in the refrigerant flow direction.
  • the nozzle part 14a is an isentropic decompression of the refrigerant in the refrigerant passage formed inside.
  • the refrigerant passage formed in the nozzle portion 14a includes a throat portion that reduces the passage cross-sectional area the most, and a divergent portion in which the passage cross-sectional area gradually increases from the throat toward the refrigerant injection port that injects the refrigerant. Is formed. That is, the nozzle part 14a of this embodiment is configured as a Laval nozzle.
  • the nozzle portion 14a is set such that the flow rate of the injected refrigerant injected from the refrigerant injection port during the normal operation of the cycle is equal to or higher than the sound speed.
  • the body portion 14b is made of a substantially cylindrical metal (in this embodiment, aluminum).
  • the body portion 14b functions as a fixing member that supports and fixes the nozzle portion 14a therein and forms an outer shell of the ejector 14. More specifically, the nozzle portion 14a is fixed by press-fitting so as to be housed inside the longitudinal end of the body portion 14b.
  • the body part 14b may be formed of resin.
  • a portion corresponding to the outer peripheral side of the nozzle portion 14a is formed with a refrigerant suction port 14c provided so as to penetrate the inside and the outside and communicate with the refrigerant injection port of the nozzle portion 14a.
  • the refrigerant suction port 14c is a through hole that sucks the refrigerant that has flowed out from a suction side evaporator 19 described later into the ejector 14 by the suction action of the jet refrigerant injected from the nozzle portion 14a.
  • a suction passage and a diffuser portion 14d are formed inside the body portion 14b.
  • the suction passage is a refrigerant passage that guides the suction refrigerant sucked from the refrigerant suction port 14c to the refrigerant injection port side of the nozzle portion 14a.
  • the diffuser unit 14d is a pressure increasing unit that increases the pressure by mixing the suction refrigerant and the injection refrigerant.
  • the suction passage is formed in a space between the outer peripheral side around the tapered tip of the nozzle portion 14a and the inner peripheral side of the body portion 14b, and the refrigerant passage area of the suction passage is directed toward the refrigerant flow direction. It is gradually shrinking. Thereby, the flow rate of the suction refrigerant flowing through the suction passage is gradually increased to reduce energy loss (so-called mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser portion 14d.
  • the diffuser portion 14d is a portion where a refrigerant passage extending in a truncated cone shape is formed so as to be continuous with the outlet of the suction passage.
  • the passage cross-sectional area gradually increases toward the downstream side of the refrigerant flow.
  • the diffuser part 14d converts the kinetic energy of the mixed refrigerant into pressure energy by such a passage shape.
  • the cross-sectional shape of the inner peripheral wall surface of the body portion 14b that forms the diffuser portion 14d of the present embodiment is formed by combining a plurality of curves. And since the degree of spread of the refrigerant passage cross-sectional area of the diffuser portion 14d gradually increases in the refrigerant flow direction and then decreases again, the refrigerant can be increased in an isentropic manner.
  • the refrigerant inlet side of the outflow side evaporator 18 is connected to the outlet of the diffuser portion 14d.
  • the outflow side evaporator 18 exchanges heat between the refrigerant flowing out from the diffuser portion 14d and the blown air blown from the indoor blower 18a toward the vehicle interior, evaporating the refrigerant and exerting an endothermic effect, thereby generating blown air. It is a heat exchanger for endothermic cooling.
  • the indoor blower 18a is an electric blower in which the rotation speed (that is, the amount of blown air) is controlled by a control voltage output from the air conditioning control device 40. Furthermore, the suction port side of the compressor 11 is connected to the refrigerant outlet side of the outflow side evaporator 18.
  • the flow rate adjustment valve 20 is an integrated (in other words, modularized) cycle component device surrounded by a broken line in FIG. More specifically, the flow rate adjusting valve 20 is an integrated unit of the suction side pressure reducing device 15, the bypass passage 16, the variable throttle device 17, and the like.
  • the suction-side decompression device 15 is a suction-side decompression unit that decompresses the other refrigerant branched by the branching unit 13 until it becomes a low-pressure refrigerant.
  • the suction-side decompression device 15 is a variable throttle configured to be able to change the passage cross-sectional area (that is, the throttle opening) of the throttle passage 20a that decompresses the refrigerant.
  • the suction side decompression device 15 causes the decompressed refrigerant to flow out to the refrigerant inlet side of the suction side evaporator 19 described later.
  • the bypass passage 16 bypasses the refrigerant on the inlet side of the suction-side decompression device 15 (more specifically, the throttle passage 20a) by bypassing the suction-side decompression device 15, and more specifically, the suction-side decompression device 15 (more specifically, This is a refrigerant passage that leads to the outlet side of the throttle passage 20a) (in other words, the refrigerant inlet side of the suction-side evaporator 19).
  • the variable throttle device 17 is a variable throttle mechanism that adjusts the flow rate of the refrigerant flowing through the bypass passage 16 (specifically, the mass flow rate and other flow rates are the same). Furthermore, the variable throttle device 17 has a function of opening and closing the bypass passage 16. More specifically, the variable throttle device 17 opens the bypass passage 16 when the flow rate Ge1 of the refrigerant flowing out from the suction side pressure reducing device 15 is equal to or lower than a predetermined reference flow rate KGe1.
  • the reference flow rate KGe1 is based on the temperature distribution of the blown air cooled by the suction side evaporator 19 when the variable throttle device 17 closes the bypass passage 16 and reduces the flow rate of the circulating refrigerant circulating in the cycle. It is set to a value that expands beyond the temperature difference.
  • the temperature distribution of the blown air is defined by a temperature difference obtained by subtracting the minimum temperature from the maximum temperature of the blown air immediately after being cooled by the suction side evaporator 19. Furthermore, the reference temperature difference is set to a value at which the occupant begins to feel uncomfortable due to the temperature distribution.
  • the detailed configuration of the flow rate adjusting valve 20 will be described with reference to FIGS.
  • the up and down arrows in FIGS. 2 to 4 indicate the up and down directions when the flow rate adjusting valve 20 is mounted on the vehicle.
  • the flow regulating valve 20 has a body part 21.
  • the body part 21 is formed by combining a plurality of constituent members made of metal (in this embodiment, made of aluminum).
  • the body portion 21 forms an outer shell of the flow rate adjusting valve 20 and functions as a housing that accommodates some of the components such as the suction side pressure reducing device 15 and the variable throttle device 17 therein.
  • the body part 21 may be formed of resin.
  • various refrigerant passages such as a bypass passage 16, a throttle passage 20a, and a temperature sensing passage 20b are formed inside the body portion 21 .
  • the outer surface of the body portion 21 is provided with a plurality of refrigerant inlets and outlets such as a refrigerant inlet 21a, an evaporator side outlet 21b, an evaporator side inlet 21c, and a low pressure outlet 21d.
  • the other refrigerant outlet side of the branch part 13 is connected to the refrigerant inlet 21a.
  • the refrigerant inlet 21 a is a refrigerant inlet through which the other refrigerant branched at the branching portion 13 flows.
  • the refrigerant inlet 21 a communicates with the inlet side of the throttle passage 20 a of the suction side pressure reducing device 15 and the inlet side of the bypass passage 16 inside the body portion 21.
  • the refrigerant inlet side of the suction side evaporator 19 is connected to the evaporator side outlet 21b.
  • the evaporator side outlet 21 b is a refrigerant outlet through which the refrigerant decompressed by the suction side decompression device 15 and the refrigerant that has passed through the bypass passage 16 flow out to the refrigerant inlet side of the suction side evaporator 19.
  • the refrigerant outlet side of the suction side evaporator 19 is connected to the evaporator side inlet 21c.
  • the evaporator side inlet 21c is a refrigerant inlet through which the refrigerant flowing out from the suction side evaporator 19 flows into the temperature sensitive passage 20b.
  • the refrigerant suction port 14c side of the ejector 14 is connected to the low pressure outlet 21d.
  • the low-pressure outlet 21d is a refrigerant outlet through which the refrigerant flowing through the temperature-sensitive passage 20b flows out to the refrigerant suction port 14c side.
  • the suction side pressure reducing device 15 has a throttle passage 20a, a throttle valve 51, a drive mechanism 52, and the like.
  • the throttle passage 20a is a refrigerant passage that depressurizes the other refrigerant branched at the branching portion 13 by reducing the passage cross-sectional area.
  • the throttle passage 20a is formed in a rotating body shape such as a hemispherical shape or a truncated cone shape.
  • the throttle passage 20a of the present embodiment is formed integrally with the body portion 21.
  • the throttle passage 20a may be formed by fixing an orifice formed of a separate member to the body portion 21 to the body portion 21 by means such as press fitting.
  • the throttle valve 51 is formed in a spherical shape, and changes the minimum passage sectional area (that is, the throttle opening) of the throttle passage 20a by being displaced in the central axis direction of the throttle passage 20a. Furthermore, the throttle passage 20a can be closed by bringing the throttle valve 51 into contact with the outlet of the throttle passage 20a.
  • the throttle valve 51 receives a load on the side for reducing the throttle opening of the throttle passage 20a from a coil spring 52e which is an elastic member.
  • the drive mechanism 52 is a drive unit that displaces the throttle valve 51 in the central axis direction of the throttle passage 20a.
  • the drive mechanism 52 is a mechanical mechanism.
  • the drive mechanism 52 has a temperature sensing part 52a in which a diaphragm 52b, which is a deforming member that deforms in accordance with the temperature and pressure of the refrigerant flowing out from the suction side evaporator 19, is arranged.
  • the deformation of the diaphragm 52 b is transmitted to the throttle valve 51 via the operating rod 53, thereby displacing the throttle valve 51.
  • the diaphragm 52b divides the space formed in the temperature sensing part 52a into an enclosed space 52c and an introduction space 52d.
  • a temperature-sensitive medium whose pressure changes with a change in temperature is enclosed.
  • the temperature-sensitive medium is mainly composed of a refrigerant circulating in the ejector refrigeration cycle 10.
  • the temperature sensing part 52a is fixed to the body part 21 so that the introduction space 52d communicates with the temperature sensing passage 20b.
  • the pressure of the temperature sensitive medium in the enclosed space 52c changes according to the temperature of the refrigerant flowing through the temperature sensitive passage 20b (that is, the refrigerant flowing out of the suction side evaporator 19).
  • transforms according to the pressure difference of the pressure of the refrigerant
  • the diaphragm 52b is formed of a material that is rich in elasticity and excellent in pressure resistance and airtightness. Therefore, in this embodiment, a circular metal thin plate made of stainless steel (specifically, SUS304) is employed as the diaphragm 52b.
  • SUS304 stainless steel
  • the diaphragm 52b may be made of rubber (eg, ethylene propylene diene rubber or hydrogenated nitrile rubber) containing a base fabric (eg, polyester).
  • the saturation pressure of the temperature sensing medium in the enclosed space 52c of the drive mechanism 52 rises, and the enclosed space
  • the pressure difference between the pressure of the refrigerant flowing through the temperature sensing passage 20b increases from the pressure of the temperature sensing medium in 52c.
  • the throttle valve 51 is displaced to the side that increases the throttle opening of the throttle passage 20a.
  • the drive mechanism 52 can displace the throttle valve 51 in accordance with the temperature and pressure of the refrigerant on the outlet side of the suction-side evaporator 19 in the same manner as a so-called temperature expansion valve. In other words, the drive mechanism 52 can displace the throttle valve 51 according to the degree of superheat of the refrigerant on the outlet side of the suction side evaporator 19.
  • the throttle valve 51 is displaced so that the superheat degree SH1 of the refrigerant on the outlet side of the suction side evaporator 19 approaches a predetermined reference superheat degree KSH1 (specifically, 0 ° C.).
  • the suction side pressure reducing device 15 changes the throttle opening so that the superheat degree SH1 of the refrigerant on the outlet side of the suction side evaporator 19 approaches the reference superheat degree KSH1.
  • the reference superheat degree KSH1 can be adjusted by changing the load of the coil spring 52e.
  • the bypass passage 16 is formed by a part of the first passage 16a formed in the body portion 21 and the second passage 16b.
  • the first passage 16a is formed so as to connect the inlet side of the suction side pressure reducing device 15 (specifically, the inlet side of the throttle passage 20a) and the temperature sensitive passage 20b.
  • the first passage 16a is formed in a substantially cylindrical shape. The central axis of the first passage 16 a extends in parallel with the displacement direction of the throttle valve 51.
  • the second passage 16b is formed so as to connect the first passage 16a and the outlet side of the suction side decompression device 15 (specifically, the outlet side of the throttle passage 20a).
  • the second passage 16b is formed in a substantially cylindrical shape.
  • path 16b is extended in the direction perpendicular
  • a substantially cylindrical valve body 17a constituting the variable throttle device 17 is disposed inside the first passage 16a.
  • a communication passage that connects the first passage 16a and the second passage 16b is formed in the valve body portion 17a.
  • the valve body portion 17a is displaced in the direction of the central axis of the first passage 16a to open and close the bypass passage 16 by opening and closing the inlet portion of the second passage 16b. Further, the valve body portion 17a is displaced in the direction of the central axis of the first passage 16a, and the passage opening area of the variable passage device 17 as a whole is changed by changing the passage cross-sectional area of the inlet portion of the second passage 16b.
  • the valve body portion 17a circulates through the inlet-side pressure receiving surface that receives the inlet-side pressure Pri, which is the pressure of the refrigerant flowing from the refrigerant inlet 21a (that is, the refrigerant on the inlet side of the suction-side decompression device 15), and the temperature sensing passage 20b. It has an outlet side pressure receiving surface that receives the outlet side pressure Peo which is the pressure of the refrigerant (that is, the refrigerant flowing out of the suction side evaporator 19).
  • the area of the inlet side pressure receiving surface and the area of the lower stage pressure receiving surface are set to be approximately equal.
  • a seal member such as an O-ring is interposed in the gap between the inner peripheral surface of the first passage 16a and the outer peripheral surface of the valve body portion 17a, and the refrigerant does not leak from the gap between these members. Further, the valve body 17a receives a load on the side where the bypass passage 16 is opened from a coil spring 17b which is an elastic member.
  • variable throttle device 17 of the present embodiment when the pressure difference ⁇ P is larger than a predetermined reference pressure difference K ⁇ P, as shown in FIG. 2, the coil spring 17b is pushed and contracted. The valve body portion 17a is displaced so that the bypass passage 16 is closed.
  • valve body portion 17a When the pressure difference ⁇ P becomes equal to or less than the reference pressure difference K ⁇ P, as shown in FIG. 3, the valve body portion 17a is connected to the first passage 16a and the second passage 16b by the load of the coil spring 17b. Displace to. Then, by slightly opening the inlet portion of the second passage 16b, a throttle state in which a pressure reducing action is exerted is achieved.
  • the throttle opening is increased. Then, as shown in FIG. 4, the valve body portion 17a is displaced until the passage cross-sectional area of the inlet portion of the second passage 16b is maximized, so that the bypass passage 16 is fully opened.
  • the pressure difference ⁇ P at which the flow rate Ge1 of the refrigerant flowing out from the suction-side decompression device 15 becomes the reference flow rate KGe1 is set to the reference pressure difference K ⁇ P.
  • the variable throttle device 17 opens the bypass passage 16 when the flow rate Ge1 of the refrigerant flowing out from the suction side pressure reducing device 15 is equal to or less than the reference flow rate KGe1.
  • the reference pressure difference K ⁇ P can be adjusted by changing the load of the coil spring 17b.
  • the refrigerant inlet side of the suction side evaporator 19 is connected to the evaporator side outlet 21 b of the flow rate adjusting valve 20.
  • the suction-side evaporator 19 exchanges heat between the refrigerant that has flowed out of the evaporator-side outlet 21b of the flow rate adjustment valve 20 and the blown air that has passed through the outflow-side evaporator 18, and evaporates the refrigerant to exert a heat absorption effect.
  • An endothermic heat exchanger that cools blown air.
  • the refrigerant outlet of the suction side evaporator 19 is connected to the evaporator side inlet 21c side of the flow rate adjustment valve 20.
  • the refrigerant suction port 14 c side of the ejector 14 is connected to the low pressure outlet 21 d of the flow rate adjusting valve 20.
  • the refrigerant outlet of the suction side evaporator 19 is connected to the refrigerant suction port 14 c side of the ejector 14 via the temperature sensing passage 20 b of the flow rate adjusting valve 20.
  • each of the outflow side evaporator 18 and the suction side evaporator 19 of the present embodiment are integrally configured.
  • each of the outflow side evaporator 18 and the suction side evaporator 19 includes a plurality of tubes that circulate the refrigerant, and a collection or distribution of refrigerants that are arranged at both ends of the plurality of tubes and circulate through the tubes.
  • a so-called tank-and-tube heat exchanger having a pair of collective distribution tanks.
  • the outflow side evaporator 18 and the suction side evaporator 19 are integrated by forming the collective distribution tank of the outflow side evaporator 18 and the suction side evaporator 19 with the same member.
  • the outflow side evaporator 18 and the suction side evaporator 19 are connected in series with the blowing air flow so that the outflow side evaporator 18 is arranged upstream of the blowing air flow with respect to the suction side evaporator 19. Is arranged. Accordingly, the blown air flows as shown by the arrows drawn by the two-dot chain line in FIG.
  • the air conditioning control device 40 (not shown) is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, and performs various calculations and processing based on an air conditioning control program stored in the ROM. The operation of the various control target devices 11, 12a, 18a connected to is controlled.
  • an inside air temperature sensor that detects the vehicle interior temperature Tr
  • an outside air temperature sensor that detects the outside air temperature Tam
  • a solar radiation sensor that detects the amount of solar radiation As in the vehicle interior
  • a blowout from the suction-side evaporator 19 A group of sensors for air conditioning control such as an evaporator temperature sensor for detecting the blown air temperature (evaporator temperature) Tefin is connected, and detection values of these air conditioning sensor groups are input.
  • an operation panel (not shown) is connected to the input side of the air conditioning control device 40, and operation signals from various operation switches provided on the operation panel are input to the air conditioning control device 40.
  • an air conditioning operation switch that requests air conditioning
  • a vehicle interior temperature setting switch that sets the vehicle interior temperature, and the like are provided.
  • the air conditioning control device 40 of the present embodiment is configured such that a control unit that controls the operation of various devices to be controlled connected to the output side is integrally configured.
  • a configuration (hardware and software) for controlling the operation of the control target device constitutes a control unit of each control target device.
  • the configuration for controlling the operation of the compressor 11 constitutes a discharge capacity control unit.
  • the air-conditioning control device 40 executes an air-conditioning control program stored in advance to control the operations of the various control target devices 11, 12a, and 18a.
  • the target blowing temperature TAO of the blown air blown into the vehicle interior is calculated based on the detection signal of the sensor group for air conditioning control and the operation signal from the operation panel. And based on the target blowing temperature TAO etc., the operating state of each control object apparatus is determined. For example, about the compressor 11, it determines so that a refrigerant
  • the target blowing temperature TAO is a value having a correlation with the amount of heat that the ejector refrigeration cycle needs to generate in order to keep the passenger compartment at a desired temperature (in other words, the heat load of the ejector refrigeration cycle 10). . Therefore, when cooling the passenger compartment, reducing the refrigerant discharge capacity of the compressor 11 as the target blowing temperature TAO increases increases the refrigerant discharge capacity of the compressor 11 as the cooling heat load decreases. It means to lower.
  • the air conditioning control device 40 decreases the refrigerant discharge capacity of the compressor 11 as the cooling heat load decreases, the flow rate of the circulating refrigerant that circulates in the cycle decreases, and the refrigerant flowing out of the suction-side decompression device 15 decreases.
  • the flow rate Ge1 also decreases.
  • the refrigerant discharge capacity of the compressor 11 is lowered with a decrease in the cooling heat load, the inlet side pressure Pri is lowered and the pressure difference ⁇ P is also reduced.
  • the operating condition in which the cooling heat load is relatively high and the flow rate Ge1 of the refrigerant flowing out from the suction-side decompression device 15 is larger than the reference flow rate KGe1 is defined as normal operation.
  • the normal operation is performed when the outside air temperature is relatively high, for example, in summer.
  • an operation condition in which the cooling heat load is relatively low and the refrigerant flow rate Ge1 flowing out from the suction-side decompression device 15 is equal to or lower than the reference flow rate KGe1 is defined as low load operation.
  • the low load operation is executed, for example, when the outside air temperature is relatively low, such as in spring or autumn, or when anti-fogging of the vehicle window is performed at the low outside air temperature.
  • the air conditioning control device 40 When the air conditioning control device 40 operates the compressor 11, the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12.
  • the refrigerant flowing into the radiator 12 exchanges heat with the outside air blown from the cooling fan 12a, and is cooled and condensed.
  • the flow of the refrigerant flowing out of the radiator 12 is branched at the branching section 13.
  • One refrigerant branched by the branch part 13 flows into the nozzle part 14 a of the ejector 14.
  • the refrigerant that has flowed into the nozzle portion 14a of the ejector 14 is decompressed in an isentropic manner at the nozzle portion 14a and is injected from the refrigerant injection port of the nozzle portion 14a. Then, the refrigerant that has flowed out of the suction-side evaporator 19 by the suction action of the injected refrigerant is sucked from the refrigerant suction port 14 c through the temperature sensing passage 20 b of the flow rate adjustment valve 20.
  • the injection refrigerant injected from the refrigerant injection port of the nozzle portion 14a and the suction refrigerant sucked from the refrigerant suction port 14c flow into the diffuser portion 14d.
  • the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area.
  • the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant increases.
  • the refrigerant whose pressure has been increased in the diffuser section 14d flows into the outflow side evaporator 18.
  • the refrigerant that has flowed into the outflow evaporator 18 absorbs heat from the air blown by the indoor blower 18a and evaporates. Thereby, the blowing air blown by the indoor blower 18a is cooled. The refrigerant flowing out from the outflow side evaporator 18 is sucked into the compressor 11 and compressed again.
  • the other refrigerant branched at the branching section 13 flows into the refrigerant inlet 21 a of the flow rate adjusting valve 20.
  • the variable throttle device 17 closes the bypass passage 16
  • the total flow rate of the refrigerant flowing into the refrigerant inlet 21 a of the flow rate adjusting valve 20 is reduced by the suction side pressure reducing device 15 to adjust the flow rate. It flows out from the evaporator side outlet 21b of the valve 20.
  • variable throttle device 17 opens the bypass passage 16, so that the refrigerant flowing into the refrigerant inlet 21 a of the flow rate adjustment valve 20 is decompressed by both the suction side decompression device 15 and the bypass passage 16. Then, it flows out from the evaporator side outlet 21b of the flow rate adjusting valve 20.
  • the superheat degree SH1 of the refrigerant on the outlet side of the suction-side evaporator 19 approaches the reference superheat degree KSH1 during normal operation and low load operation regardless of load fluctuations.
  • the throttle opening is adjusted.
  • the refrigerant that has flowed out of the evaporator side outlet 21 b of the flow rate adjusting valve 20 flows into the suction side evaporator 19.
  • the refrigerant flowing into the suction side evaporator 19 absorbs heat from the blown air after passing through the outflow side evaporator 18 and evaporates. Thereby, the blast air after passing the outflow side evaporator 18 is further cooled.
  • the refrigerant that has flowed out of the suction side evaporator 19 is sucked from the refrigerant suction port 14c.
  • the outflow side evaporator 18 and the suction side evaporator 19 can be used in the vehicle interior during normal operation and low load operation regardless of load fluctuations. It is possible to cool the blown air sent to the air.
  • the refrigerant whose pressure has been increased by the diffuser portion 14d of the ejector 14 is sucked into the compressor 11 via the outflow side evaporator 18.
  • the consumption power of the compressor 11 is reduced and the coefficient of performance of the cycle is reduced compared to the normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the suction refrigerant sucked into the compressor are substantially equal. (COP) can be improved.
  • variable throttle device 17 of the flow rate adjusting valve 20 closes the bypass passage 16 during normal operation. Therefore, during normal operation, the suction side decompression device 15 adjusts the throttle opening, so that the refrigerant on the outlet side of the suction side evaporator 19 can be a gas phase refrigerant having a superheat degree.
  • variable throttle device 17 of the flow rate adjustment valve 20 opens the bypass passage 16 during low load operation, so the suction side pressure reducing device 15 reduces the throttle opening. Even so, the refrigerant that has passed through the bypass passage 16 can surely flow out to the inlet side of the suction side evaporator 19. Therefore, it is possible to suppress a shortage of the flow rate of the refrigerant flowing into the suction side evaporator 19 during the low load operation.
  • the flow rate adjustment valve 20 of the present embodiment when applied to the ejector refrigeration cycle 10, the flow rate of the refrigerant flowing into the suction-side evaporator 19 is appropriately adjusted according to cycle load fluctuations. be able to.
  • the flow rate adjustment valve 20 is provided, so that the flow rate of the refrigerant flowing into the suction-side evaporator 19 is appropriately adjusted according to the cycle load fluctuation. be able to.
  • variable throttle device 17 of the flow rate adjusting valve 20 of the present embodiment increases the throttle opening as the pressure difference ⁇ P decreases. Therefore, the flow rate of the refrigerant flowing out to the inlet side of the suction side evaporator 19 through the bypass passage 16 can be increased with the decrease in the flow rate Ge1 of the refrigerant flowing out from the suction side decompression device 15. According to this, the flow rate of the refrigerant flowing into the suction side evaporator 19 can be more appropriately adjusted according to the cycle load fluctuation.
  • FIG. 5 is a view in which the variable throttle device 17 of the present embodiment opens the bypass passage 16 in the fully open state, similarly to FIG. 4 described in the first embodiment.
  • the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.
  • one end portion of the first passage 16a of the bypass passage 16 is the inlet side of the suction side pressure reducing device 15 (specifically, the inlet side of the throttle passage 20a).
  • the other end of the first passage 16a does not communicate with the temperature sensing passage 20b.
  • the inner peripheral surface of the first passage 16a and the valve body portion 17a so that the pressure Psp in the spring chamber 17c in which the coil spring 17b is accommodated is equal to the refrigerant pressure on the outlet side of the throttle passage 20a.
  • a part of the sealing member interposed in the gap with the outer peripheral surface of is omitted.
  • the valve body part 17a of this embodiment is displaced according to the pressure difference which subtracted the pressure Psp in the spring chamber 17c from the inlet side pressure Pri and the load received from the coil spring 17b.
  • the pressure Psp in the spring chamber 17c is highly responsive in accordance with the change in the refrigerant pressure on the outlet side of the throttle passage 20a. It does not change and becomes a substantially constant value. For this reason, the valve body 17a of the present embodiment is displaced substantially according to the load generated by the inlet side pressure Pri and the load received from the coil spring 17b.
  • the valve body 17a When the inlet pressure Pri becomes equal to or lower than the reference pressure KPri, the valve body 17a is displaced to a position where the first passage 16a and the second passage 16b are communicated with each other by the load of the coil spring 17b. Set to the aperture state.
  • the throttle opening is increased as the inlet pressure Pri decreases.
  • the valve body part 17a is displaced until the channel
  • the inlet side pressure Pri at which the flow rate Ge1 of the refrigerant flowing out from the suction side pressure reducing device 15 becomes the reference flow rate KGe1 is set to the reference pressure KPri.
  • the variable throttle device 17 opens the bypass passage 16 when the flow rate Ge1 of the refrigerant flowing out from the suction side pressure reducing device 15 is equal to or lower than the reference flow rate KGe1.
  • the reference pressure KPri can be adjusted by changing the load of the coil spring 17b.
  • variable throttle device 17 of the flow rate adjustment valve 20 closes the bypass passage 16. Further, during the low load operation of the ejector refrigeration cycle 10, the variable throttle device 17 of the flow rate adjustment valve 20 opens the bypass passage 16.
  • the flow rate adjusting valve 20 of the present embodiment when applied to the ejector refrigeration cycle 10, the flow rate adjusting valve 20 flows into the suction-side evaporator 19 according to the load fluctuation of the cycle, as in the first embodiment.
  • the flow rate of the refrigerant can be adjusted appropriately.
  • the flow rate adjustment valve 20 is provided, so that the flow rate of the refrigerant flowing into the suction-side evaporator 19 is appropriately adjusted according to the cycle load fluctuation. be able to.
  • variable throttle device 17 of the flow rate adjusting valve 20 of the present embodiment increases the throttle opening as the inlet side pressure Pri decreases. Therefore, the flow rate of the refrigerant flowing out to the inlet side of the suction side evaporator 19 through the bypass passage 16 can be increased with the decrease in the flow rate Ge1 of the refrigerant flowing out from the suction side decompression device 15. According to this, the flow rate of the refrigerant flowing into the suction side evaporator 19 can be more appropriately adjusted according to the cycle load fluctuation.
  • FIG. 6 is a view in which the variable throttle device 17 of the present embodiment opens the bypass passage 16 in the fully open state, similarly to FIG. 4 described in the first embodiment.
  • the throttle opening can be increased with higher accuracy than the second embodiment as the inlet pressure Pri decreases.
  • a part of the first passage 16a of the bypass passage 16 is formed in a rotating body shape such as a hemispherical shape or a truncated cone shape similar to the throttle passage 20a. Yes. Furthermore, the same spherical body as the throttle valve 51 is adopted as the valve body portion 17d. The valve body portion 17d receives a load on the side of reducing the partial cross-sectional area of the first passage 16a from the coil spring 17b.
  • the minimum passage sectional area (that is, the throttle opening) of the first passage 16a can be changed by displacing the valve body portion 17d. Further, the first passage 16a can be closed by bringing the valve body portion 17d into contact with the first passage 16a.
  • the flow rate adjusting valve 20 of the present embodiment has a drive mechanism 71 for the variable throttle device 17 as a drive unit that drives and displaces the valve body portion 17d.
  • the basic configuration of the drive mechanism 71 for the variable aperture device 17 is the same as that of the drive mechanism 52.
  • the drive mechanism 71 has a temperature sensing part 72.
  • the temperature sensing unit 72 includes a diaphragm 72b that is a deformable member that partitions the space in the temperature sensing unit 72 into an enclosed space 72c and an introduction space 72d.
  • An inert gas in this embodiment, nitrogen gas
  • the introduction space 72d of the drive mechanism 71 is fixed to the body portion 21 so as to communicate with the inlet side of the suction side pressure reducing device 15 (specifically, the throttle passage 20a).
  • the diaphragm 72b deforms according to the pressure difference between the pressure of the refrigerant on the inlet side of the suction-side decompression device 15 and the pressure of the inert gas in the enclosed space 72c. Further, the drive mechanism 71 displaces the valve body portion 17d by transmitting the deformation of the diaphragm 72b to the valve body portion 17d via the operating rod 73.
  • the volume change due to the temperature of the inert gas is relatively small. For this reason, even if the temperature and the outside air temperature of the inlet side of the suction side decompression device 15 introduced into the introduction space 72d change, the pressure of the inert gas in the enclosed space 72c becomes substantially constant. Therefore, in the variable throttle device 17 of the present embodiment, the throttle opening can be increased with a decrease in the inlet-side pressure Pri with higher accuracy than in the second embodiment.
  • a reference medium temperature (this embodiment) determined in advance from the pressure of the refrigerant flowing through the temperature sensing passage 20b of the flow rate adjusting valve 20 and flowing out from the low-pressure outlet 21d (that is, outlet-side pressure Peo).
  • a value obtained by subtracting the saturation pressure of the temperature sensitive medium at 0 ° C. is defined as the valve opening set pressure Y.
  • a detailed method for measuring the valve opening set pressure Y will be described later.
  • the maximum value of the passage sectional area of the suction side pressure reducing device 15 is defined as the maximum throttle sectional area Aex
  • the minimum value of the passage sectional area of the bypass passage 16 is defined as the minimum passage sectional area Apt.
  • the ratio (Apt / Aex) of the maximum passage sectional area Apt to the maximum throttle sectional area Aex is defined as an area ratio X.
  • the maximum throttle cross-sectional area Aex can be determined based on the maximum circulation flow rate of the refrigerant circulating in the cycle. Therefore, in the flow regulating valve 20, the area ratio X can be changed mainly by changing the minimum passage sectional area Apt.
  • the area ratio X increases, the ratio of the flow rate of the refrigerant flowing into the suction side evaporator 19 via the bypass passage 16 tends to increase. For this reason, if the area ratio X is set to be large, the superheat degree SH1 of the refrigerant on the outlet side of the suction side evaporator 19 is changed to the reference superheat degree KSH1 even if the suction side pressure reducing device 15 changes the throttle opening during normal operation. There is a risk that it will be difficult to approach.
  • the area ratio X decreases, the ratio of the flow rate of the refrigerant flowing into the suction side evaporator 19 via the bypass passage 16 decreases. For this reason, if the area ratio X is set to a small value, the flow rate of the refrigerant flowing into the suction side evaporator 19 may be insufficient when the suction side pressure reducing device 15 reduces the throttle opening degree during low load operation. is there.
  • valve opening set pressure Y of the flow rate adjusting valve 20 is related to the flow rate of the refrigerant flowing from the flow rate adjusting valve 20 to the suction side evaporator 19, and the valve opening set pressure is set.
  • Y we examined how to determine the area ratio X systematically.
  • valve opening set pressure Y in the present embodiment is determined in advance from the “expansion valve outlet pressure” in the “Testing method for static superheat of expansion valves for automobile air conditioners” in the “Standard of the Japan Refrigeration and Air Conditioning Industry Association”. This corresponds to a pressure obtained by subtracting the saturation pressure of the temperature-sensitive medium in the enclosed space 52c at the reference medium temperature (0 ° C. in the present embodiment).
  • the pressure Py of the refrigerant flowing out from the low pressure outlet 21d of the flow rate adjustment valve 20 is measured, and the valve opening set pressure Y is determined using this value. ing.
  • the inlet side of the pressure vessel BT is connected to the evaporator side outlet 21b of the flow rate adjusting valve 20, and the evaporator side inlet 21c of the flow rate adjusting valve 20 is connected to the outlet side of the pressure vessel BT.
  • the pressure vessel BT forms a buffer space corresponding to the suction side evaporator 19.
  • a pressure vessel BT having an internal volume of the buffer space of 0.001 m 3 is employed.
  • the pressure Py of the air flowing out from the low pressure outlet 21d of the flow rate adjusting valve 20 is measured using the temperature of the temperature sensitive medium in the enclosed space 52c as the reference medium temperature.
  • an orifice that causes a predetermined pressure loss is measured in order to measure the pressure Py.
  • the pressure Py is substantially a pressure corresponding to the outlet-side pressure Peo that is the pressure of the refrigerant that has flowed out of the suction-side evaporator when the ejector refrigeration cycle 10 is operated.
  • the valve opening set pressure Y is determined by subtracting the saturation pressure of the temperature sensitive medium that is the reference medium temperature from the pressure Py.
  • valve opening set pressure Y is adjusted by changing the load of the coil spring 52e, similarly to the reference superheat degree KSH1.
  • the area ratio X may be decreased as the valve opening set pressure Y is set to a high value.
  • the throttle opening of the suction side pressure reducing device 15 decreases. Therefore, the area ratio X may be increased as the valve opening set pressure Y is set to a low value.
  • the present inventors set the area ratio X and the valve opening set pressure Y so as to satisfy the following formulas F1 and F2 during normal operation, so that an appropriate flow rate can be obtained. It was confirmed that the refrigerant could be supplied to the suction side evaporator 19.
  • the present inventors determine the area ratio X and the valve opening set pressure Y so as to satisfy the formulas F1 and F3 (so as to enter the shaded hatched region in FIG. 9) as a practically effective range. ing.
  • the maximum throttle cross-sectional area Aex, the minimum passage cross-sectional area Apt, and the load of the coil spring 52e are adjusted so as to satisfy the expressions F1 and F3.
  • the area ratio X and the valve opening set pressure are set so that the ratio of the flow rate of the refrigerant flowing into the suction-side evaporator 19 via the bypass passage 16 does not unnecessarily increase during normal operation.
  • Y is determined.
  • the area ratio X and the valve opening set pressure Y are determined so that the flow rate of the refrigerant flowing into the suction-side evaporator 19 is not insufficient during low load operation.
  • the refrigerant decompressed by the suction-side decompression device 15 regardless of load fluctuations, whether during normal operation or during low load operation. And the refrigerant that has passed through the bypass passage 16 can flow out from the evaporator-side outlet 21 b and flow into the suction-side evaporator 19.
  • the suction side pressure reducing device 15 increases the throttle opening. For this reason, the ratio of the flow rate of the refrigerant flowing into the suction side evaporator 19 via the suction side pressure reducing device 15 in the flow rate of the refrigerant flowing into the suction side evaporator 19 increases. In other words, regarding the change in the flow rate of the refrigerant flowing into the suction-side evaporator 19, the degree of influence of the change in the throttle opening degree of the suction-side decompression device 15 increases.
  • the area ratio X and the valve opening set pressure Y are set so as to satisfy the above formula F1. Therefore, even if the bypass passage 16 is not closed, the suction side pressure reducing device 15 changes the throttle opening so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator 19 approaches the reference superheat degree. The flow rate of the refrigerant flowing into the suction side evaporator 19 can be adjusted.
  • the suction-side pressure reducing device 15 decreases the throttle opening degree under the operating condition in which the flow rate of the refrigerant flowing into the suction-side evaporator 19 is relatively small as in the low-load operation. For this reason, the ratio of the flow rate of the refrigerant that has passed through the bypass passage 16 in the flow rate of the refrigerant flowing into the suction side evaporator 19 increases. In other words, regarding the change in the flow rate of the refrigerant flowing into the suction-side evaporator 19 during the low load operation, the degree of influence of the change in the throttle opening degree of the suction-side decompression device 15 becomes small.
  • the area ratio X and the valve opening set pressure Y are set so as to satisfy the above formula F3. Therefore, at the time of low load operation, even if the suction side pressure reducing device 15 reduces the throttle opening, the refrigerant that has passed through the bypass passage 16 can surely flow into the suction side evaporator 19. Thereby, it can suppress that the flow volume of the refrigerant
  • the flow rate adjustment valve 20 of the present embodiment when applied to the ejector refrigeration cycle 10, the flow rate of the refrigerant flowing into the suction-side evaporator 19 is appropriately adjusted according to cycle load fluctuations. be able to.
  • the flow rate adjustment valve 20 is provided, so that the flow rate of the refrigerant flowing into the suction-side evaporator 19 is appropriately adjusted according to the cycle load fluctuation. be able to.
  • the above formulas F1 and F2 are differential pressures obtained by subtracting the area ratio X, which is a dimensionless number, and the saturation pressure determined by the physical properties of the refrigerant from the outlet side pressure Peo. Since the valve opening set pressure Y is used, it is also confirmed that the present invention is applicable to a wide range of refrigerants without being limited to R1234yf.
  • the ejector refrigeration cycle 10 that employs a wide variety of refrigerants is suitable for both normal operation and low load operation. It is possible to allow a refrigerant having a proper flow rate to flow into the suction side evaporator 19.
  • the refrigerant on the inlet side of the suction-side decompression device 15 is led to the outlet side of the suction-side decompression device 15 by bypassing the suction-side decompression device 15.
  • the example in which the bypass passage 16 is arranged has been described, but the arrangement of the bypass passage 16 is not limited to this.
  • the bypass passage 16 is formed. It may be shortened.
  • a nozzle side pressure reducing device 25 is added to the ejector refrigeration cycle 10 as shown in the overall configuration diagram of FIG. 11 with respect to the first embodiment.
  • the nozzle side pressure reducing device 25 is a variable throttle mechanism that reduces the pressure of the refrigerant branched by the branching portion 13 on the upstream side of the nozzle portion 14a. Further, the nozzle-side pressure reducing device 25 functions as a flow rate adjusting device that adjusts the flow rate of the refrigerant flowing into the nozzle portion 14a.
  • the basic configuration of the nozzle side pressure reducing device 25 is the same temperature type expansion valve as the suction side pressure reducing device 15 described in the first embodiment.
  • the superheat degree SH of the refrigerant on the outlet side of the outflow side evaporator 18 (that is, the suction refrigerant sucked into the compressor 11) is a predetermined nozzle side reference superheat degree KSH (in this embodiment, The throttle opening is displaced so as to approach 1 ° C.
  • an intermediate pressure reducing device 26 is added to the ejector refrigeration cycle 10 as shown in the overall configuration diagram of FIG. 12 with respect to the first embodiment.
  • the intermediate pressure depressurization device 26 is a variable throttle mechanism that depressurizes the refrigerant flowing out of the radiator 12 until it becomes an intermediate pressure refrigerant on the upstream side of the branch portion 13. Further, the intermediate pressure reducing device 26 functions as a flow rate adjusting device that adjusts the flow rate of the refrigerant flowing into the branch portion 13.
  • the basic configuration of the intermediate pressure reducing device 26 is the same temperature type expansion valve as the suction side reducing device 15 described in the first embodiment.
  • the superheat degree SH of the refrigerant on the outlet side of the outflow side evaporator 18 (that is, the suction refrigerant sucked into the compressor 11) is a predetermined nozzle side reference superheat degree KSH (in this embodiment, The throttle opening is displaced so as to approach 1 ° C.
  • the gas-liquid separator 27 is a gas-liquid separator that stores the excess liquid-phase refrigerant separated by separating the gas-liquid of the refrigerant that has flowed out of the diffuser portion 14d.
  • the inlet side of the nozzle portion 14 a of the ejector 14 is connected to the outlet of the radiator 12.
  • the gas-phase refrigerant outlet of the gas-liquid separator 27 is connected to the suction port side of the compressor 11, and the liquid-phase refrigerant outlet of the gas-liquid separator 27 is connected to the refrigerant inlet 21 a side of the flow rate adjusting valve 20. Yes.
  • the air conditioning control device 40 operates the compressor 11, the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12.
  • the refrigerant flowing into the radiator 12 exchanges heat with the outside air blown from the cooling fan 12a, and is cooled and condensed.
  • the refrigerant that has flowed out of the radiator 12 flows into the nozzle portion 14 a of the ejector 14.
  • the refrigerant that has flowed into the nozzle portion 14a of the ejector 14 is decompressed in an isentropic manner at the nozzle portion 14a and is injected from the refrigerant injection port of the nozzle portion 14a. Then, the refrigerant that has flowed out of the suction-side evaporator 19 by the suction action of the injected refrigerant is sucked from the refrigerant suction port 14 c through the temperature sensing passage 20 b of the flow rate adjustment valve 20.
  • the injection refrigerant injected from the refrigerant injection port of the nozzle portion 14a and the suction refrigerant sucked from the refrigerant suction port 14c flow into the diffuser portion 14d.
  • the refrigerant whose pressure has been increased in the diffuser section 14 d flows into the gas-liquid separator 27.
  • the gas-phase refrigerant separated by the gas-liquid separator 27 is sucked into the compressor 11 and compressed again.
  • the liquid phase refrigerant separated by the gas-liquid separator 27 flows into the refrigerant inlet 21 a of the flow rate adjustment valve 20.
  • the refrigerant decompressed by the suction side decompression device 15 flows out from the evaporator side outlet 21b of the flow rate adjustment valve 20 and flows into the suction side evaporator 19. To do. Further, during low load operation, the refrigerant decompressed by the suction side decompression device 15 and the refrigerant that has passed through the bypass passage 16 flow out from the evaporator side outlet 21 b of the flow rate adjustment valve 20 and flow into the suction side evaporator 19. To do.
  • the refrigerant flowing into the suction side evaporator 19 absorbs heat from the blown air blown by the indoor blower 18a and evaporates. Thereby, the blowing air blown by the indoor blower 18a is cooled. The refrigerant that has flowed out of the suction side evaporator 19 is sucked from the refrigerant suction port 14c.
  • the blown air blown into the vehicle interior by the suction-side evaporator 19 during normal operation and low load operation regardless of load fluctuations. Can be cooled. And the effect similar to the ejector-type refrigerating cycle 10 demonstrated in 1st Embodiment can be acquired.
  • the flow rate adjusting valve 20 can appropriately adjust the flow rate of the refrigerant flowing into the suction side evaporator 19 even when applied to the ejector refrigeration cycle 10a.
  • the flow rate adjustment valve 20 is provided, so that the flow rate of the refrigerant flowing into the suction-side evaporator 19 is appropriately adjusted according to the cycle load fluctuation. be able to.
  • the present invention is not limited to this.
  • the same effect can be obtained even if the ejector refrigeration cycle 10, 10a includes the suction side pressure reducing device 15, the bypass passage 16, and the variable throttle device 17 as separate components.
  • the branching unit 13, the ejector 14, and the like may be integrated with the flow rate adjusting valve 20.
  • the present invention is not limited to this.
  • the spring chamber 17c may be communicated with the outside air, and the pressure Psp of the spring chamber 17c may be set to the external pressure.
  • the spring chamber 17c may be evacuated.
  • a seal member may be disposed in the gap between the inner wall surface of the first passage 16a and the valve body portion 17a.
  • bypass passage 16 may be a relatively short distance extending from immediately before the throttle passage 20a to the downstream side of the throttle passage 20a.
  • the bypass passage 16 may be formed by cutting out a part of the inner peripheral surface of the portion of the body 21 where the throttle passage 20a is formed.
  • Each component device constituting the ejector refrigeration cycle 10 is not limited to that disclosed in the above-described embodiment.
  • an electric compressor is employed as the compressor 11
  • the compressor 11 is driven by a rotational driving force transmitted from a vehicle traveling engine via a pulley, a belt, or the like.
  • An engine driven compressor may be employed.
  • the variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or the refrigerant discharge capacity can be adjusted by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch A fixed-capacity compressor can be employed.
  • the receiver integrated condenser which has the receiver part (in other words, liquid receiver) which stores the condensed refrigerant
  • FIG. May be adopted.
  • the branch portion 13 is not limited to this.
  • a centrifugal type gas-liquid separator structure may be adopted as the branching section 13.
  • the refrigerant having a relatively high dryness on the turning center side is caused to flow out to the nozzle portion 14a side of the ejector 14, and the refrigerant having a relatively low dryness on the outer peripheral side is caused to flow out to the refrigerant inlet 21a side of the flow rate adjusting valve 20. May be.
  • outflow side evaporator 18 and the suction side evaporator 19 are integrally configured.
  • the outflow side evaporator 18 and the suction side evaporator 19 are configured separately. Also good.
  • different refrigerant target fluids may be cooled in different temperature zones.
  • R1234yf is adopted as the refrigerant
  • the refrigerant is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • a supercritical refrigeration cycle in which carbon dioxide is employed as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.
  • the ejector refrigeration cycle 10 is applied to a vehicle air conditioner, but application of the ejector refrigeration cycle 10 is not limited thereto.
  • the present invention may be applied to stationary air conditioners, cold storages, other cooling and heating devices, and the like.
  • each of the above embodiments may be appropriately combined within a practicable range.
  • the flow rate adjusting valve 20 described in the second to fourth embodiments may be applied to the ejector refrigeration cycles 10 and 10a described in the fifth to seventh embodiments.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

Ce cycle de réfrigération à éjecteur comprend un compresseur (11), un condenseur (12), un éjecteur (14), une unité de dépressurisation côté admission (15), un évaporateur côté admission (19), un passage de dérivation de guidage (16), et un mécanisme d'étranglement variable (17). L'unité de dépressurisation côté admission dépressurise un fluide frigorigène. L'évaporateur côté admission amène le fluide frigorigène détendu par l'unité de dépressurisation côté admission à s'évaporer et à s'écouler vers le côté orifice d'admission du fluide frigorigène. Le passage de dérivation amène le fluide frigorigène sur le côté d'entrée de l'unité de dépressurisation côté admission à contourner l'unité de dépressurisation côté admission et à guider ledit fluide frigorigène vers le côté d'entrée de l'évaporateur côté admission. Le mécanisme d'étranglement variable règle le débit du fluide frigorigène s'écoulant dans le passage de dérivation. L'unité de dépressurisation côté admission modifie l'ouverture d'étranglement de telle sorte que le degré de surchauffe (SH1) du fluide frigorigène sur le côté de sortie de l'évaporateur côté admission approche d'un degré de surchauffe de référence prédéterminé (KSH1). Le mécanisme d'étranglement variable a pour fonction d'ouvrir et de fermer le passage de dérivation, et ouvre le passage de dérivation si le débit (Ge1) du fluide frigorigène s'écoulant hors de l'unité de dépressurisation côté admission n'est pas supérieure à un débit de référence prédéterminé (KGe1).
PCT/JP2019/000270 2018-02-08 2019-01-09 Cycle de réfrigération à éjecteur et soupape de réglage de débit WO2019155805A1 (fr)

Applications Claiming Priority (4)

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JP2018-020762 2018-02-08
JP2018020762 2018-02-08
JP2018-091449 2018-05-10
JP2018091449A JP7031482B2 (ja) 2018-02-08 2018-05-10 エジェクタ式冷凍サイクル、および流量調整弁

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021199864A1 (fr) * 2020-04-03 2021-10-07 株式会社デンソー Structure de montage de soupapes d'expansion

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006118849A (ja) * 2004-09-22 2006-05-11 Denso Corp エジェクタ式冷凍サイクル
JP2007040586A (ja) * 2005-08-02 2007-02-15 Denso Corp エジェクタ式冷凍サイクル
JP2007078339A (ja) * 2005-06-30 2007-03-29 Denso Corp エジェクタ式冷凍サイクル
JP2009162444A (ja) * 2008-01-08 2009-07-23 Denso Corp 蒸気圧縮式サイクル
JP2017219262A (ja) * 2016-06-08 2017-12-14 株式会社デンソー エジェクタ式冷凍サイクル装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006118849A (ja) * 2004-09-22 2006-05-11 Denso Corp エジェクタ式冷凍サイクル
JP2007078339A (ja) * 2005-06-30 2007-03-29 Denso Corp エジェクタ式冷凍サイクル
JP2007040586A (ja) * 2005-08-02 2007-02-15 Denso Corp エジェクタ式冷凍サイクル
JP2009162444A (ja) * 2008-01-08 2009-07-23 Denso Corp 蒸気圧縮式サイクル
JP2017219262A (ja) * 2016-06-08 2017-12-14 株式会社デンソー エジェクタ式冷凍サイクル装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021199864A1 (fr) * 2020-04-03 2021-10-07 株式会社デンソー Structure de montage de soupapes d'expansion
JP7447644B2 (ja) 2020-04-03 2024-03-12 株式会社デンソー 膨張弁の取付構造

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